JPH06185549A - Machine operation type disc brake - Google Patents

Abstract

PURPOSE: To provide a fully mechanically operated type disk brake being economical in terms of manufacture and installation as compared with hydraulically operated types and capable of equalizing friction. CONSTITUTION: This disk brake comprises fixed bodies 1, 2 with openings which form cylindrical seats 9; pistons 10, 11 and friction pads 12, 13 all of which together constitute braking shoes; and disks 17, 18 for pressing the pistons 10, 11 via combinations of cutouts 21, 24 and balls 22, 23. An operating lever comprising a pair of arms 30, 31 connected to a traction element and rigidly connected to the pistons 10, 11 is provided at approximately the center of the disk brake and a braking disk is sandwiched and disposed between the pistons 10, 11. Operation of the traction element causes rotation of the lever, that is, the arms, thereby moving the pistons 10, 11 in mutually approaching directions so that the braking disk is held and compressed by the friction pads 12, 13. When the operation of the traction element is stopped, the arms 30, 31 act elastically to release braking action.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a mechanically actuated disc brake, and more particularly to a mechanically actuated disc brake for motorcycles such as bicycles, mopeds and motorcycles.

[0002]

BACKGROUND OF THE INVENTION As is well known, disc brakes include a disc rigidly coupled to the wheel to be braked to which two opposing fluid or mechanical actuated shoes are attached. It is pressed and absorbs the kinetic energy of the wheel by friction.

Fluid actuated disc brakes suffer from a certain amount of structural complexity due to the need to actually provide a hydraulic system.

Mechanically actuated disc brakes are known from DE-A 2522625, DE 3043700 and DE 1530500, 1630244 and 22229481. In the disc brakes described in these documents, an actuating lever is provided, which actuates the brake shoe via an eccentric element or screw when rotated by the user. When the shoe is moved axially (e.g. at right angles to the disc), the shoe abuts the face of the disc and reacts to move the other shoe onto the other face of the disc, which causes the disc to shoe. Clamped and braked between. This type of brake has the serious problem that the stroke of the actuating lever determines the axial movement of the two pads, so that such a stroke is quite large and the stroke increases rapidly as the wear of the pads progresses. British Patent No. 1528967 and German Patent Publication No. 27
No. 54099 discloses a disc brake in which a lever is associated with each shoe and acts on each shoe via an eccentric element. In these brakes, when the lever is actuated, the pad carries out a movement with a radial and a tangential component on the disc, so that the axial thrust point is not constant in the center of the pad and therefore the pad is wedge-shaped. Wear, which increases the displacement of the thrust point and causes severe pad deterioration.

[0005]

SUMMARY OF THE INVENTION The technical object of the present invention is to provide a fully mechanically actuated disc brake which is more economically advantageous than hydraulically actuated disc brakes in terms of its manufacture and installation. Is to provide.

[0006]

The object of the invention is to provide a mechanically actuated disc brake: a fixed body defining an opening, through which the brake disc rotates and two opposite coaxial shafts, respectively. A fixed body where a seat of the seat is opened in the direction of the opening; a piston that forms a brake shoe that is provided with a friction pad and is guided in the seat; and a brake operation lever that includes a pair of arms. A brake actuating lever, each arm having an end rigidly rotationally coupled to a respective piston and coupled to a traction element; and means disposed between the piston and the body. When the lever is rotated in one rotation direction by operating the traction element, the pistons are axially moved toward each other and the friction pad is moved. Means for engaging with the brake disc, and elastically exerting a force on the piston to pull the piston away from the brake disc when the operation of the traction element is stopped. Is achieved by a mechanically actuated disc brake such that the arm is formed as described above.

Other advantages and features of the invention will be apparent from the following description of the accompanying drawings.

[0008]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT In FIGS. 1-5, reference numerals 1 and 2 designate two shoe elements constituting a brake body. The element 2 is fixed to the raised portion 3 of the element 1 by means of screws 4. The raised portion 3 forms an opening 5 between the shoes 1 and 2 through which the brake disc 6 rotates. The body of the brake is fixed to a fixed part of the vehicle (bicycle, moped, motorcycle) or other structure by means of a screw 7 screwed into the element 1, so that the center plane A of the brake coincides with the plane of the disc 6. To do.

Formed in opposite faces of the elements 1 and 2 are two cylindrical sheets 8 and 9, which are coaxial with one another with respect to an axis B perpendicular to the face A and the aperture 5 Open in the direction of.

Two cylindrical pistons 10 and 11 are axially guided in the seats 8 and 9 and have two friction pads 12 and 13 on their opposite faces. The friction pad 12
And 13 are fixed by screws 14 and 15 so as to act on both sides of the disk 6. The friction pads are not touching the disc 6 when the pistons 10 and 11 are fully inserted into the seats 8 and 9. The pistons 10 and 11 and the pads 12 and 13 form the brake shoes of the brake.

Seats 16 and 16a for the disks 17 and 18 that abut the bottoms of the seats 8 and 9 are formed in the pistons 10 and 11 opposite the friction pads 12 and 13. The disks 17 and 18 have three radial grooves 17a, 18a on their faces that abut the bottoms of the seats 8 and 9,
Respective teeth 19 and 19a projecting from the bottom of the are engaged with the three radial grooves 17a, 18a. The disks 17 and 18 are thus rigidly rotationally connected to the elements 1 and 2. It is of course possible to provide other means for preventing rotation of the disks 17 and 18, as will be explained later in FIGS. 6, 7 and 8.

A set of three notches 20 is formed in the face of the disk 17 adjacent to the piston 10; said notches being equidistantly spaced about axis B and extending.
Using the direction C of axis B (FIG. 5) as the viewing direction, the notch 20 in the disk 17 has a depth that decreases counterclockwise.

Similarly, a set of three notches 21 similar to notch 20 but clockwise is formed in the bottom of seat 16. Each notch 20 faces a respective notch 21, so that three balls 22 whose radius is slightly larger than the depth of the notches 20 and 21 are engageable in the notches facing each other.

Also located between the disc 18 and the piston 11 is a ball 23, which engages the notches 24 and 25 of the disc 18 and the piston 11, the depth of these notches being notches 20 and 21. Just like the above, respectively, it decreases in the counterclockwise direction and the clockwise direction, respectively.

The ends of the pistons 10 and 11 on the same side as the pads 12 and 13 project into the opening 5 and have a pair of recesses 26 and 27 formed in the periphery. The recesses of each pair are arranged diametrically with respect to the axis B and are lateral and open on the front face of the piston.

Pistons 10 and 1 projecting into the opening 6
Rings 28 and 29 are arranged around one end and are integral with the respective arms 30 and 31 which are tangentially joined with the ring to form a brake operating lever. . Each ring 28
And 29 have diametrically opposed internal teeth 32 and 3
3 are provided, the internal teeth 32 and 33 of which are recesses 2
Dimensioned to engage within 6 and 27 to provide a rotational connection with pistons 10 and 11.

The arms 30 and 31 are rigidly connected to each other by a pin 34, which penetrates through the ends of the arms 30 and 31 and also acts as a hinge pin for the strip 35, on which strip 35 is actuated. A conventional screw 36 is provided for connecting the traction element D, for example a cable, for The traction element D is guided in a perforated bolt 37, which is screwed in the plane A into a wing 38 projecting from the raised portion 3 of the element 1. The perforated bolt 37 has a recessed head for abutting the guide sheath of the traction element D as usual.

Arms 30 and 31 are broken lines 39 and 40.
And 39a, 40a (see FIGS. 2, 5, 9 and 10) they have a bifurcated configuration which produces a lateral elastic force when the brake is not actuated. The elastic force exerts a force on the rings 28 and 29 to act on the pistons 10 and 11 to push them into their respective seats 8 and 9 to hold the pistons 10 and 11 apart. Line 39, 40
And 39a, 40a are parallel to each other and approximately perpendicular to the line connecting the center of the ring to the pin 34.

The operation of the above brake is as follows.

In the non-actuated state, the brake is in the position as shown in FIGS. 1 to 3, in which position the balls 22 and 23 have notches 20, 2 as shown in FIG.
Engaged within the deepest areas of 1 and 24, 25.
In this position the pistons 10 and 11 are in the arm 3
The elastic expansion forces of 0 and 31 pull them apart, thus allowing the disc 6 to rotate freely.

When the brake is actuated and the traction element D is operated, the arms 30 and 31 swing toward the position shown by the broken line in FIG.
1. Rotate 1 with respect to disks 17 and 18.

As a result, the balls 22 and 23 are rolled along the slope portion formed by the bottom portions of the notches 20, 21 and 24, 25. In this way (see FIG. 4), the pistons 10 and 11 are subjected to axial movement in the direction towards each other, which brings the pads 12 and 13 into contact with the disc 6 for a braking effect.

If the traction element D is released, the polygonal line 3
A bifurcated elastic preload obtained by arms 30 and 31 via 9, 40 and 39a, 40a and via the flexure generated by the movement of pistons 10 and 11 acts on said piston to force it into seat 8
And pull it in 9 However, notch 2
The shapes of 0, 21 and 24, 25 generate a tangential component, which creates a screwing movement of the pistons 10 and 11, which screwing movements of the arms 30 and 31.
To return to the initial position.

The basic advantage of the above-mentioned brake is that during the stroke of the pistons 10 and 11 towards the disc they are pushed by the balls 22 and 23 in a direction exactly perpendicular to the plane A. It is configured. Moreover, the strokes of the pistons are always equal.
In this way the pad is evenly worn and not subject to wedge wear.

The brakes described above can have numerous modifications and variations.

FIG. 6 shows how the rotational coupling of the disks 17 and 18 is provided by square pins 41 and 42 which prismaticly engage in the corresponding square holes of the disks 17 and 18.

Further, a friction pad is partially embedded in the recesses 43 and 44 of the piston and the friction pad is provided with peripheral teeth 45 and 46, which are peripheral teeth 45 and 4.
Rotation of the pad is prevented by the engagement of 6 in the recess around the corresponding recess.

A lubricating fluid is enclosed in an intermediate space formed between the disks 17 and 18 and the respective pistons 10 and 11, while it is embedded in the annular grooves of the seats 8 and 9 and abuts the outer surface of the pistons. Sealing rings 47 and 48 that are present prevent the ingress of dust or debris which would tend to impair the functionality of the brake.

In the embodiment of FIG. 7, the disks 17 and 18 are provided with peripheral teeth 49 and 50 which engage in the notches of the seats 8 and 9 to prevent rotation of said disks. is doing. Furthermore, the disc has central pins 51 and 52 which serve as guides for the pistons 10 and 11, on the outside of which the sealing rings 53 and 54 rest. Reference numerals 55 and 56 denote recesses formed on the front surface of the piston to accommodate the friction pad.

By providing two parallel flat portions 57 and 58 (see FIG. 8) on the periphery of each pad, the pad is prevented from rotating and the flat portions 57 and 58 are recessed 5.
A prismatic anti-rotation bond is formed by mating with the respective flat portions of the peripheral walls of 5 and 56. Sheets 59 and 60 suitable for preventing leakage of lubricant are preferably inserted between the pads 12 and 13 and the piston.

In another embodiment of the disc brake according to the invention, the axial movement of the piston is formed by providing a threaded connection of the piston in the seats 8 and 9, whereby the notches 20, 21 of the previous embodiment. And 24, 25 and balls 22 and 23 have similar effects.

In another embodiment, the thrust imparted to the bifurcated structure of arms 30 and 31 includes the disk 6
It is obtained by inserting a spring acting between the arms 30 and 31 on the outside of the arm to spread the arm.

According to the preferred embodiment shown in FIGS. 8, 9 and 10, two walls 61 and 62 parallel to the axis B in each of the recesses 26 and 27 and a circular wall 63 lying in a plane perpendicular to the axis B are provided. And are provided. A tooth 64 with circular ends extends axially from the central region of each circular wall 63 in the direction of the front of the respective piston 10 and 11, i.e. in the direction of the pads 12 and 13.

The internal teeth 32 and 38 of the rings 28 and 29 abut the ends of the teeth 64. In this way, the rings 28 and 29 do not come into contact with the circular wall 63 due to the elastic thrust of the arms 30 and 31 acting on the two diametrically opposed fulcrums of the pistons, whereby the pistons 10 and 11 Prevents the pistons 10 and 11 from jamming due to imbalances in the axial thrust as they are drawn into the seats 8 and 9.

As can be seen from FIGS. 9 and 11, the polygonal lines 39, 40 and 39a, 40a show that the faces of the rings 28 and 29 include an angle α with respect to the face A, which is the arm 3
It is preferably provided so as to be smaller than the angle β included by 0 and 31. Actually the angles α and β
Is ring 2 when the brake is not operating.
The faces of 8 and 29 intersect face A on the side of the pin 34 connecting the arms 30 and 31 (see FIG. 9), while the pad 1
The plane of the ring is chosen to intersect plane A on the opposite side of pin 34 to axis B when 2 and 13 are in contact with brake disc 6 (FIG. 10).

The teeth 32 and 33 of each pair are arranged in a plane E perpendicular to the axis B and, in the position where the brake is not actuated, a plane F which divides the swing angle γ of the arms 30 and 31 into two equal parts. (See FIG. 11).

[0037]

As described above, the mechanically actuated disc brake according to the present invention can be made much more economical in terms of manufacturing and mounting than the hydraulically actuated disc brake.

[Brief description of drawings]

FIG. 1 is a side view of a brake according to the present invention.

2 is a cross-sectional view taken along the plane II-II in FIG.

FIG. 3 is a partial cross-sectional view of the brake shoe in a position where the brake is not operated.

FIG. 4 is a partial cross-sectional view of the brake shoe with the brake in the activated position.

FIG. 5 is an exploded view of a brake.

FIG. 6 is a cross-sectional view of another embodiment of the disc brake.

FIG. 7 is a sectional view of still another embodiment of the disc brake.

FIG. 8 is a detailed perspective view of a piston.

FIG. 9 is a shape view of two arms that form the lever when the brake is not in the operating position.

FIG. 10 is a shape view of two arms that form a lever when the brake is in an operating position.

11 is a side sectional view according to the plane XI-XI of FIG. 7 showing the rotational coupling between the arm and the piston.

[Explanation of symbols]

 1, 2 Fixed body 5 Opening 6 Brake disc 8, 9 Seat 10, 11 Piston 12, 13 Friction pad 17, 18 Disc 20, 21, 24, 25 Slope 22, 23 Ball 26, 27 Recess 28, 29 Ring-shaped part 30, 31 Arm 32, 33 Teeth 39, 39a, 40, 40a Polygonal line 41, 42 Center guide pin 63 Wall 64 Teeth A Disk surface B Piston shaft D Traction member E Diameter surface F Lever bisect surface α , Β Ring-brake disc angle γ Lever swing angle

Claims (11)

[Claims] 1. A mechanically actuated disc brake, especially for two-wheeled vehicles such as bicycles, mopeds and motorcycles, in which the fixed body (1, 1) forms an opening (5).
2) the stationary body, wherein the brake disc (6) rotates through the opening and the two opposing coaxial respective seats (8, 9) open in the direction of the opening (1, 2); a piston (10, 11) having a friction pad (12, 13) and constituting a brake shoe guided in the seat; and a pair of arms (30, 3)
1) A brake actuating lever comprising 1), each arm having an end rigidly rotationally connected to a respective piston (10, 11) and connected to a traction element (D). And; and means (20-25) arranged between the piston (10, 11) and the body (1, 2), wherein the lever is rotated in one rotation direction by operating a traction element. The means (20-) for axially moving the pistons (10, 11) towards each other when engaged to engage a friction pad (12, 13) with the brake disc (6).
25) and; including pads (12, 13) when the operation of the traction element is stopped
The arm (30, 3) so as to elastically exert a force on the piston (10, 11) to separate the piston (10, 11) from the brake disc (6).
1) is formed; a mechanically actuated disc brake, characterized in that 2. A ring-shaped part (2) provided with means (32, 33) for the arm (30, 31) to make a rotational connection to the respective piston (10, 11).
8. 29), characterized in that the arm (30, 31) is constituted by an elastic lamella to which a preload is applied so as to press the piston (10, 11) into the disengaged position. 1 disc brake. 3. The rotary coupling means comprises the ring (2)
, 29) a pair of diametrically formed teeth (3
2, 33), which engage a respective recess (26, 27) formed around the piston (10, 11) and open laterally and on the front of the piston. Disc brake according to claim 2, characterized in that it comprises teeth (32, 33). 4. A wall (63) in which the recesses (26, 27) are arranged in a plane perpendicular to the axis (B) of the piston, and teeth (6) extending from the center of the wall towards the front of the piston.
4), said teeth (64) of two diametrically arranged recesses (26, 27) acting as support fulcrums for the respective rings (28, 29). Disc brake of item 3. 5. The ring (28, 29) is a disc (6).
Angle (α) with respect to the plane (A), and the angle (β) included with respect to the plane by the arms (30, 31)
The arm (30, 31) has two polygonal lines (39, 39a, 40, 40a) so as to be smaller, and the corner (α,
β), when the brake is not actuated, the ring (28, 29) intersects the surface (A) of the disc (6) on one side of the axis (B) of the piston (10, 11) and the brake is applied. The disc brake of claim 4, wherein when actuated, the two sides are crossed on the opposite side. 6. Brakes in which the teeth (32, 33) arranged inside the rings (28, 29) are diametrical faces (E) passing through the axis (B) of the pistons (10, 11). In a non-actuated position, the diametrical surface (E) is oriented such that the surface (E) is substantially perpendicular to the surface (F) that bisects the lever swing angle (γ). The disc brake of claim 3, wherein the disc brake is located within 7. The arm (30, 31) has a ring (28,
29) is tangentially joined to; and said fold line (39, 39a, 40, 40a) is substantially perpendicular to the line connecting the center of the ring to the connection point of the traction element. The disc brake according to claim 6, which is characterized in that. 8. The means for axially moving a piston comprises a plurality of balls (22,23), said balls comprising the piston (10,11) and the bottom of the seat (8,9). Having rolling engagement on a beveled portion (20, 21, 24, 25) formed between opposing faces of the seat (8, 9) and the piston (10, 11), the beveled surface being Disc brake according to claim 1, characterized in that the parts (20, 21, 24, 25) are adapted to move the shoe into a position for engagement with the brake disc (6). 9. A disc (17,1) in which the bottom of the seat is rigidly rotationally connected to the respective seat (8,9).
The disc brake according to claim 8, which is constituted by 8). 10. A center guide pin (41, 4) for said piston (10, 11), said discs (17, 18).
The disc brake according to claim 9, further comprising 2). 11. The piston comprises a friction pad (12,
Disc brake according to claim 10, characterized in that 13) has a recess (55, 56) embedded therein so that it is rigidly rotationally coupled.